Derailleur for a bicycle

ABSTRACT

A derailleur for a bicycle comprises; a fixing member; a transformable linkage mechanism comprising a base member, two linkage members and a movable member; and a chain guide having a guide pulley and a tension pulley. The linkage mechanism is supported swingably to the fixing member in the relation that the guide pulley reciprocates away from or toward the axis of the sprocket assembly. The derailleur is provided between the chain guide and the movable member with a first spring, between the fixing member and the linkage mechanism with a second spring for biasing the guide pulley away from the axis of sprocket assembly, and with a forcibly moving mechanism which moves the chain guide axially of the sprocket assembly and also radially thereof in a plane perpendicular to the axis of the sprocket assembly.

FIELD OF THE INVENTION

This invention relates to a derailleur for a bicycle, and moreparticularly to a derailleur for a bicycle, which is provided with afixing member, a linkage mechanism or pantograph mechanism comprising abase member, two linkage members and a movable member, and a chain guidehaving a guide pulley and a tension pulley, the pantograph mechanismbeing transformed by a control wire so as to reciprocate the chain guideto thereby shift a driving chain to a desired sprocket at a multistagesprocket assembly for changing the bicycle speed.

BACKGROUND OF THE INVENTION

Conventionally, in order to improve the speed change efficiency of aderailleur, a first spring is interposed between the chain guide and themovable member and a second spring is interposed between the base memberand the fixing member, so that the first and second springs providetension to the chain and are balanced with each other to set the chainguide in position with respect to each sprocket.

The second spring biases the pantograph mechanism clockwise with respectto the fixing member, in other words, biases the guide pulley radiallyoutwardly from the multistage sprocket assembly, and the chain guide,even when shifting the chain, has a tendency to move under a springforce of the second spring so that an interval between the guide pulleyand the smaller diameter sprocket becomes larger than that between theguide pulley and the larger diameter sprocket. As a result, the properinterval, even when set with respect to the larger diameter sprocket, istoo large as the interval for the smaller diameter one. Especially, whena difference in diameters of both sprockets is larger, the intervalbetween the guide pulley and the smaller diameter sprocket is too muchlarger, thereby creating a problem in that the speed change efficiencydeteriorates.

In order to solve the above problem, it is proposed that the secondspring is reduced in its spring force so as to set the chain guide to bereduced in the interval betewen the guide pulley and the smallerdiameter sprocket. The reduced interval, however, in some cases maycause an interference of the guide pulley with the larger diametersprocket when the chain is shifted thereto.

In the construction where the guide pulley is controlled in position byuse of a balance between both the springs, the control capacity issmaller and the spring force of each spring should correspond to adifference in tooth number between the larger and smaller diametersprockets. Also the first spring increases in its resilience as thedifference in tooth number increases, whereby the second spring shouldalso increase its spring force for preventing the guide pulley fromcontacting wtih the larger diameter sprocket when the chain is shiftedthereto. As a result, when the first and second springs are set toobtain the interval of the predetermined length between the guide pulleyand the larger diameter sprocket, and when the chain is shifted to thesmaller diameter sprocket, the second spring of increased spring forcemakes the interval between the guide pulley and the smaller diametersprocket too large, which is an unavoidable problem.

On the other hand, the Japanese Patent Publication No. Sho 42-23,485discloses a derailleur in which connecting pins for connecting thelinkage members and base member and the movable member and linkagemember, are slanted with respect to a plane perpendicular to the axis ofthe multistatge sprocket assembly, the chain guide being forcibly movedradially of the sprocket assembly in the plane parallel to the axis ofthe same.

This construction, however, requires the chain guide to move in aspecific direction so that, when the sprocket assembly is changed, thenon-uniform intervals between each sprocket may deteriorate the speedchange efficiency.

SUMMARY OF THE INVENTION

An object of the invention is to provide a derailleur which uses thefirst and second springs and a forcibly moving mechanism for the chainguide so that the position thereof, shifted forcibly by the movingmechanism, is adjusted by balancing the first and second springs witheach other, whereby even when the multistage sprocket assembly changesits sprocket arrangement, if a difference between the diameters ofsmaller diameter and larger diameter sprockets is especially larger, orif a diameter of a sprocket is larger than the predetermined value, theinterval between the guide pulley at the chain guide and each sprocketcan be kept in an allowable range.

This invention is characterized in that the bicycle derailleur providedwith a fixing member, a linkage mechanism or pantograph mechanismcomprising a base member, two linkage members and a movable member, anda chain guide having guide and tension pulleys, builds in the forciblymoving mechanism which moves the chain guide in parallel to the axis ofthe sprocket assembly and also radially thereof in the planeperpendicular to the axis of the same, supports the pantograph mechanismto the fixing member in the relation that the guide pulley is swingableaway from or toward the axis of the same, and provides the first springbetween the chain guide and the movable member, and the second springbetween the fixing member and the pantograph mechanism to thereby biasthe guide pulley to move away from the axis of the same. Thus, theforcibly moving mechanism, when a driving chain is shifted, moves thechain guide axially of the sprocket assembly and also forcibly radiallythereof and then the first and second springs balance with each other toadjust the position of the guide pulley set by the moving mechanism,thereby making it possible to keep an interval between the guide pulleyand each sprocket in an allowable range for any arrangement ofsprockets.

The forcibly moving mechanism of the invention includes twoconstructions, one of which is that the connecting pins for connectingthe linkage members to the base member and movable member are slanted tothe plane perpendicular to the axis of the multistage sprocket assemblyso as to have a so-called thrust construction, and the other is that afirst control member having a plurality of first engaging portioncorresponding to the number of speed change stages and a second controlmember having a second engaging portion engageable with each of firstengaging portions, are combined into a feed construction.

The forcibly moving mechanism in both of the above cases, when thepantograph mechanism is transformed, is made movable not only axially ofthe multistage sprocket assembly but also radially thereof in the planeperpendicular to the axis of the same.

The combination for feed construction of this invention is characterizedin that the forcibly moving mechanism is so constructed that when themechanism moves the pulley across the smaller and larger diametersprockets, an interval between the larger diameter sprocket and theguide pulley is made larger by the mechanism than that between thesmaller diameter sprocket and the guide pulley, whereby resilience ofthe second spring when the guide pulley corresponds to the largerdiameter sprocket, is made stronger than that when the same correspondsto the smaller diameter sprocket.

In this invention, the chain guide is supported swingably to the movablemember at a position shifted from the axis of rotation of the guidepulley, thereby incorporating the chain guide as the so-calledtriangular balance type into the combination for feed construction,which is a characteristic in the feed construction.

This construction can set the guide pulley in position where itcorresponds to the smaller diameter sprocket at the smallest intervalnecessary to shift the driving chain. On the other hand, when thepantograph mechanism is transformed to allow the guide pulley tocorrespond to the larger diameter sprocket, the second spring balanceswith the first spring to allow the pantograph mechanism to swing withrespect to the fixing member from the interval set by the forciblymoving mechanism, thereby allowing the guide pulley to approach thelarger diameter sprocket and adjusting the inverval between the guidepulley and the larger diameter sprocket corresponding thereto. Hence, itis possible to improve the shifting of the driving chain especially tothe smaller diameter sprocket as well as to the larger diameter one.

These and other objects, features and advantages of the invention willbecome more apparent upon a reading of the following detaileddescription and drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a front view of a first embodiment of a derailleur of theinvention mounted together with a multistage sprocket assembly to thebicycle frame,

FIG. 2 is a side view of the FIG. 1 embodiment,

FIGS. 3 and 4 are illustrations of the operation of the FIG. 1embodiment,

FIG. 5 is an illustration of spring characteristics of first and secondsprings used in the FIG. 1 embodiment,

FIG. 6 is a partially omitted front view of the derailleur of theinvention, corresponding to FIG. 1,

FIGS. 7 through 10 are views of a second embodiment of the derailleur ofthe inveniton, in which

FIG. 7 is a front view of the second embodiment, corresponding to FIG.1,

FIG. 8 is a partially cutaway bottom view of the same,

FIG. 9 is a partially omitted rear view of the same,

FIG. 10 is an illustration of the operation of the same, and

FIGS. 11 and 12 are views of a third embodiment of the derailleur of theinvention, in which

FIG. 11 is a front view of the third embodiment, corresponding to FIG.1, and

FIG. 12 is a side view of the same, corresponding to FIG. 2.

DETAILED DESCRIPTION OF THE INVENTION

The first embodiment of the invention, as shown in FIGS. 1 through 6, isa rear derailleur mounted to the rear wheel of the bicycle for use witha multistage sprocket assembly.

The rear derailleur comprises a fixing member 1, a pantograph mechanismA comprising; a base member 2, two linkage members 3 and 4 and a movablemember 5; and a chain guide 6 having a guide pulley 61 and a tensionpulley 62; the fixing member 1 being fixed to a fork end H of thebicycle as shown in FIG. 1, the base member 2 being supported to thefixing member 1 through a first horizontal shaft 7.

The base member 2 supports at one side a pair of mounting segmentsopposite to each other, the linkage members 3 and 4 being pivoted to themounting segments through a pair of pins 8 and 9, the movable member 5being pivoted to the free ends of linkage members 3 and 4 through a pairof pins 10 and 11 respectively.

The movable member 5 is shaped like the base member 2 and is provided atone side with a pair of mounting segments opposite to each other pivotedto the linkage members 3 and 4 and supports at the other side the chainguide 6 rotatably in a predetermined range only through a secondhorizontal shaft 13 parallel to the first shaft 7.

A return spring (not shown) is interposed between the linkage member 3and 4 and the movable member 5 or base member 2 to thereby bias thechain guide 6 axially of the multistage sprocket assembly, normallytoward the smaller diameter sprocket S₁.

The first embodiment supports the base member 2 swingably to the fixingmember 1 through the first shaft 7 in the relation that the guide pulley61 moves in reciprocation away from or toward the axis of sprocketassembly S (in the direction of the arrow Z in FIG. 1). Between a guideframe 63 of chain guide 6 and the movable member 5 is provided a firstspring 13 biasing the chain guide 6 clockwise in FIG. 1 with respect tothe movable member 5 and between the fixing member 1 and the base member2 is provided a second spring 14 biasing the guide pulley 61 to moveaway from the axis of sprocket assembly S (clockwise in FIG. 1). Aforcibly moving mechanism is provided which, when the pantographmechanism A is transformed, moves the guide pulley 61 axially ofsprocket assembly S and radially thereof in the plane perpendicular tothe axis of the same.

The forcibly moving mechanism has the connecting pins 8, 9, 10 and 11slanted to the plane perpendicular to the axis of sprocket assembly S sothat, when the pantograph mechanish A is transformed, the chain guide 6is moved axially of sprocket assembly S and also radially thereof in theplane perpendicular to the axis of the same.

Also, the guide drame 63 is supported swingably to the movable member 5at a position apart from the axis of guide pulley 61, thereby formingthe so-called triangular balance.

In the aforesaid construction, the path of guide pulley 61 moved by theforcibly moving mechanism across the smaller diameter sprocket S₁ andlarger diameter sprocket S₂ is so constructed that an interval l₂between the guide pulley 61 and the sprocket S₂ is made larger than thel₁ between the same and the sprocket S₁ as shown in FIGS. 3 and 4.Hence, the resilience of second spring 14, when the guide pulley 61corresponds to the larger diameter sprocket S₂, is made larger than thatof the spring 14 when the same corresponds to the smaller diametersprocket S₁.

Also, the first and second springs 13 and 14 balance with each other toadjust the guide pulley 61 in position set radially of sprocket assemblyS by the forcibly moving mechanism through the slanted pins 8 and 11,the first spring 13 giving tension to the chain and being smaller in thespring force than the second spring 14. The resilience of spring 13,when the guide pulley 61 corresponds to the sprocket S₂ through theswinging motion of chain guide 6, is made larger than that with respectto the sprocket S₁ as shown by the dotted line in FIG. 5, thereby givingconstant tension to the chain.

Although the second spring 14 biases the guide pulley 61 clockwise inFIG. 1, in other words, away from the axis of sprocket assembly S, theresilience, when the guide pulley 61 corresponds to the larger diametersprocket S₂, is made larger than that when the same corresponds to thesmaller sprocket S₁, because the forcibly moving mechanism forciblymoves the guide pulley 61 away from the sprocket S₂ correspondingthereto so that the second spring 14 balances with the first spring 13to swing the pantograph mechanism A counterclockwise in FIG. 1. Thecounterclockwise swinging motion of pantograph mechanism A allows theguide pulley 61 to approach the larger diameter sprocket S₂ as shown inFIGS. 3 and 4.

The first and second springs 13 and 14 are formed as coiled springs andare wound at intermediate portions on the horizontal shafts 12 and 7respectively, the first spring 13 being retained at one end to the chainguide 6 and at the other end to the movable member 5, the second spring14 being retained at one end to the fixing member 1 and at the other endto the base member 2.

The chain guide 6 comprises the guide pulley 61, tension pulley 62, anda guide frame 63 carrying the pulleys 61 and 62, so that the guide andtension pulleys 61 and 62 are supported, at the positions where atriangular is formed around the pivot position of guide frame 63, to themovable member 5 through the horizontal shaft 12, thereby forming theso-called triangular balance. The pulleys 61 and 62 carry the chain C asshown by the chain line in FIG. 1 and the guide pulley 61 guides thechain C to a desired one sprocket in the sprocket assembly S comprisingfive sprockets as shown.

In addition, in the drawing, a control wire W is mounted to the movablemember 5 through a fixture 15 at the pin 10 and an outer sheath Oguiding the wire W is supported to a support 16 at the pin 9.

Next, explanation wil be given of the operation of the derailleur of theinvention constructed as abovementioned.

Referring to FIGS. 1 and 2, the chain guide 6 is positionedcorresponding to the smaller diameter sprocket S₁. The control wire W ispulled to transform the pantograph mechanism A so that the forciblymoving mechanism with the slanted pins 8 through 11 moves the chainguide 6 axially of sprocket assembly S and also radially thereof in theplane perpendicular to the axis of sprocket assembly S.

At this time, the first and second springs 13 and 14 balance with eachother to actuate the pantograph mechanism A with respect to the fixingmember 1 and the chain guide 6 with respect to the movable member 5.Hence, the guide pulley 61 as shown in the dotted lines in FIGS. 3 and4, is adjusted in position radially of sprocket assembly S with respectto the position set by the forcibly moving mechanism.

In detail, when the pantograph mechanism A is transformed, the forciblymoving mechanism moves the chain guide 6 together with the movablemember 5 axially of sprocket assembly S and toward the larger diametersprocket S₂ and also radially outwardly thereof and then the interval l₂between the guide pulley 61 and the larger diameter sprocket S₂ becomeslarger than than l₁ between the same and the smaller diameter sprocketS₁.

Therefore, the first spring 13 which applies tension to the chain Cdeflects more to that extent and increases its resilience, and overcomesthe second spring 14 to swing the pantograph mechanism Acounterclockwise from the position in FIG. 1 to that in FIG. 6, wherebythe guide pulley 61 approaches the larger diameter sprocket S₂. As aresult, the guide pulley 61, as shown in FIGS. 3 and 4, is adjusted inposition with respect to the larger diameter sprocket S₂. When thepantograph mechanism A swings, the second spring 14 deflects to increaseits resilience, the swinging motion of pantograph mechanism A dependingon the balance between the first and second springs 13 and 14.

The control wire W is slackened and the return spring restores thepantograph mechanism A so that the forcibly moving mechanism with theslanted pins 8 to 11 moves the chain guide 6 axially of sprocketassembly S and also radially inwardly thereof in the plane perpendicularto the axis of the same.

In this case, the first and second springs 13 and 14 also balance witheach other so that the pantograph mechanism A operates with respect tothe fixing member 1 and the chain guide 6 operates with respect to themovable member 5.

In other words, when the pantograph mechanism A is transformed towardthe smaller diameter sprocket S₁, conversely to the above, the forciblymoving mechanism allows the guide pulley 61 to move close to the smallerdiameter sprocket S₁ and it moves to the sprocket S₁.

Hence, an amount of deflection of the first spring 13 is reduced and thesecond spring 14 overcomes the first spring 13 to return the pantographmechanism A clockwise with respect to the fixing member 1.

Such swinging motion of pantograph mechanism A causes the guide pulley61 to move away from the smaller diameter sprocket S₁, but the forciblymoving mechanism can set the pulley 61 at the smallest interval neededwith respect to the sprocket S₁.

In addition, even when the guide pulley 61 is positioned correspondingto the smaller diameter sprocket S₁ in the top speed stage, the firstand second springs 13 and 14 may be changed in the spring forces thereofto allow the pantograph mechanism A to swing counterclockwise from theposition shown in FIG. 1, thereby enabling the guide pulley 61 tofurther approach the smaller diameter sprocket S₁.

In this case, when the guide pulley 61 is positioned corresponding tothe larger diameter sprocket S₂ in the low speed stage, the resilienceof the first spring 13 increases, whereby the pantograph mechanism Amay, of course, largely swing counterclockwise.

In any case, the forcibly moving mechanism can forcibly move the chainguide 6 in the specific direction and the first and second springs 13and 14 balance with each other to swing the pantograph mechanism A withrespect to the fixing member 1, thereby enabling the guide pulley 61 tooperate corresponding to the sprocket arrangement at the sprocketassembly S. Accordingly, the moving direction of chain guide 6 by theforcibly moving mechanism can be set to reduce the interval between theguide pulley 61 and the smaller diameter one S₁ and increase thatbetween the same and the larger diameter sprocket S₂ corresponding tothe arrangement of the largest diameter sprocket applicable in practicaluse. Hence, even when the sprocket assembly changes in arrangement ofsprockets from FIG. 3 to FIG. 4, a difference in diameter between boththe larger and smaller diameter sprockets is especially larger or thelarger diameter sprocket is of diameter larger than the predeterminedvalue, the interval between the guide pulley 61 and each sprocket can bekept in a properly allowable range, thereby improving the speed changeefficiency.

Incidentally, a first sprocket assembly of smaller diameter sprocket S₁of 13 teeth and larger diameter sprocket S₂ of 28 teeth and a secondsprocket assembly of smaller diameter sprocket of 13 teeth and of largerdiameter sprocket of 18 teeth, will be described.

In this case, the interval l₁ between the guide pulley 6 and the smallerdiameter sprocket S₁ is made the smallest corresponding to the smallestdiameter sprocket of 13 teeth and the interval l₂ between the same andthe larger diameter sprocket S₂ l corresponds to the largest diametersprocket of 28 teeth and is made larger than l₁.

In a case where the guide pulley 61 is forcibly moved in order to obtainthe invervals l₁ and l₂ as abovementioned, the aforesaid embodiment canset the intervals by means of an angle of inclination of the respectiveconnecting pins 8 through 11. In a case of making the guide chain 6 thetriangular balance, the intervals depend on a balance length between thesecond horizontal shaft 12 and the axis of rotation of guide pulley 61,correspond to the multistage sprocket assembly S₁, and are affected bythe number of teeth of the front sprocket.

In the above embodiment, an angle of inclination of the respective pins8 through 11 is, for example, 30° to 40° and the balance length is 19 to22 mm.

Now, in a case of using a derailleur having an angle of inclination of40°, balance length of 22 mm, and the first and second springs 13 and 14in combination, the intervals l₁ and l₂ are given in the followingtable. Incidentally, in a case where the front sprocket of 52 teeth isused, the spring force of first spring 13 in use is 0.85 kg for thesmaller diameter sprocket S₁ of 13 teeth and 1.0 kg for the largerdiameter sprocket S₂ of 28 teeth. The second spring 14 in use, when thefront sprocket of 52 teeth is used, is 0.95 kg for the sprocket S₁ of 13teeth and 1.15 kg for the sprocket S₂ of 28 teeth for the above reason.The balance length between the second horizontal shaft 12 and the axisof rotation of tension pulley 62 is 63 mm and that between the firsthorizontal shaft 7 and the second one 12 is 58 mm.

                  TABLE                                                           ______________________________________                                                 Front Sprocket of                                                                          Front Sprocket of                                                52 Teeth     38 Teeth                                                         Interval                                                                             Interval  Interval Interval                                            1.sub.1 mm                                                                           1.sub.2 mm                                                                              1.sub.1 mm                                                                             1.sub.2 mm                                 ______________________________________                                        1st Sprocket                                                                             9.7      12.5      6.3    3                                        Assembly                                                                      (13 to 28 Teeth)                                                              2nd Sprocket                                                                             9.7      17.0      6.3    7.5                                      Assembly                                                                      (13 to 18 Teeth)                                                              Conventional                                                                             18.0     15.5      12.0   3.5                                      Example                                                                       (13 to 18 Teeth)                                                              ______________________________________                                    

As seen from the above table, among the intervals l₁ and l₂ between theguide pulley 61 and the smaller and larger diameter sprockets S₁ and S₂,especially l₂ is reducible to 6.3 mm, which has never been under 12 mm.

Incidentially, l₂ is not so different from the conventional one, but itis notable that, even when l₁ is reduced, l₂ is not so excessivelyreduced, which means that even when l₂ is made the minimum, l₁ is notexcessively enlarged.

Alternatively, the fixing member 1 may pivotably support a first controlmember 17 having a plurality of first engaging portions 17acorresponding to the number of speed change stages and the pantographmechanism A may provide a second control member 18 having a secondengaging portion 18a engageable with each of the first engaging portions17a as shown in FIGS. 7 through 10, the first and second control members17 and 18 may form the forcibly moving mechanism.

In this case, between the first control member 17 and the fixing member1 is interposed the second spring 14 biasing the pantograph mechanism Aaway from the axis of sprocket assembly S, and one of the control wire Wand outer sheath O is supported to the first control member 17 and theother to the pantograph mechanism A or a member supported thereto. Inthe above construction, the wire W in the condition shown in FIG. 7 ispulled to transform the pantograph mechanism A, then a biasing forceacting on the outer sheath O turns the first control member 17 in thedirection of deflecting the second spring 14 (counterclockwise in FIG.7) so that the engaging position of one of the first engaging portions17a with the second engaging portion 18a changes. After the change ofengaging position, when the first control member 17 is integral with thepantograph mechanism A, the restoring force of the second spring 14swings the pantograph mechanism A clockwise in FIG. 7 with respect tothe fixing member 1. Therefore, the chain guide 6 moves radiallyoutwardly of sprocket assembly S in the plane perpendicular to the axisof sprocket assembly S, thereby setting the chain guide 6 in positionradially of the same. Then, the first and second springs, 13 and 14balance with each other to actuate the pantograph mechanism A withrespect to the fixing member 1 and the chain guide 6 to the movablemember 5, so that the position of guide pulley 61 radial of sprocketassembly S is adjusted with respect to the position set by the forciblymoving system as in the first embodiment.

In addition, the first control member 17, as shown in FIG. 8 issupported rotatbly to the first horizontal shaft 7 through a sleeve 19.A plurality (six in FIG. 8) of first engaging portions 17a correspnodingto the number of speed change stages are provided at one side of athrough bore in which the shaft 7 is inserted, and a support 17b for thecontrol wire W or outer sheath O is provided at the other side. At oneside of first control member 17 is provided a rising segment 17c ofcircular arc around the first horizontal shaft 7 and extending inparallel thereto, and its edge is slanted to form thereon the firstengaging portions 17a of, for example, six steps in a continuouslystepped manner, in which a height of each step controls an axialmovement of chain guide 6 and a length of sliding face between the stepscontrols a radial movement of the same.

The second control member 18 is separate from the pantograph mechanism Aand is supported thereto through a pin 9 in relation of being movablerelative to the linkage member 4, and comprises a U-like-shaped base 18bhaving a through bore for the pin 9, a second engaging portion 18a ofpawl-like shape and extending from one end of base 18b toward the firstengaging portions 17a, and a fork 18c extending from the other end ofbase 18b toward the movable member 5, the second engaging portion 18aengaging with one of first engaging portions 17a to change an amount ofdeflection of the second spring 14, thereby setting the chain guide 6 inposition with respect to the sprocket assembly S by means of the actionof the second spring 14. An adjuster 20 is interposed between the fork18c and the linkage member 4 to thereby keep the second control member18 in position with respect to the linkage member 4.

Alternatively, in the embodiment in FIGS. 7 through 10, the firstcontrol member 17 may provide the second engaging portion and the secondcontrol member 18 may provide the first engaging portions, the first andsecond control members 17 and 18 may provide a plurality of engagingportions corresponding to the number of speed change stagesrespectively, or the engaging portions corresponding thereto may be ofslanted faces juxtaposed linearly.

Also, the first control member 17 may be pivoted to a member supportedto the fixing member 1.

The second control member 18 may be supported to the pin 8, 10 or 11,other than the pin 9, or supported to one of the base member 2, linkagemember 3 or 4, and a movable member 5.

The second spring 14 may be provided between a member supported to thefixing member 1 and the first control member 17 or a member supportedthereto, or between the fixing member 1 and a member supported to thefirst control member 17.

In addition, the control wire W or outer sheath O need only be supportedto the linkage member 3 or 4 or movable member 5.

Alternatively, the guide pulley 61 may be supported coaxially onto thesecond horizontal shaft 12 as shown in FIGS. 11 and 12.

In this case, a guide plate 63a at the guide frame 63 at the movablemember 5 side, as shown in FIG. 12, is fixed to the movable member 5 orintegral therewith.

In the above construction, since the chain guide 6 swings around thesecond horizontal shaft 12, the guide pulley 61 does not change inposition by swinging motion of chain guide 6 so that the displacement byslanted connecting pins 8 through 11 and the adjusting displacement bythe balance between first and second springs, set the guide pulley 61 inposition with respect to each sprocket.

In a case where the derailleur of the invention is used together withthe front derailleur for a front multistage sprocket assembly, even whenthe chain is switched thereby, the interval between the guide pulley 61and each sprocket at the sprocket assembly S can be kept almost uniform.

Furthermore, since the guide plate 63a can be fixed to or integral withthe movable member 5, the number of parts is reducible and looseness ofguide plate 63a from repeated use is also reduced, thereby improvingdurability to that extent.

Although several embodiments have been described, they are merelyexemplary of the invention and not to be construed as limiting, theinvention being defined solely by the appended claims.

What is claimed is:
 1. A derailleur for selectively shifting a drivingchain to one sprocket of a multistage sprocket assembly comprising,afixing member, a transformable linkage mechanism comprising a basemember, trwo linkage members and a movable member, and a chain guidesupported to said movable member and provided with a guide pulley forguiding said chain to said multistage sprocket assembly and a tensionpulley, said linkage mechanism being supported swingably to said fixingmember through a first horizontal shaft, said chain guide beingsupported swingably to said movable member through a second horizontalshaft, said derailleur having between said chain guide and said movablemember a first spring for applying tension to said chain, and betweensaid .[.fixig.]. .Iadd.fixing .Iaddend.member and said linkage mechanisma second spring for biasing said linkage mechanism in a direction ofsaid guide pulley moving away from the axis of said sprocket assembly,and being provided with a forcibly moving mechanism which, when saidlinkage mechanism is transformed, moves said guide pulley axially ofsaid sprocket assembly and radially thereof in a plane perpendicular tothe axis of said sprocket assembly.Iadd., said forcibly moving mechanismand first and second springs cooperating together such that the positionof said chainguide is forcibly shifted axially and radially of saidsprockets by said forcibly moving mechanism and the shifted position ofsaid chainguide set by said forcibly moving mechanism is radiallyadjusted with respect to said sprockets by the balancing of said firstand second springs. .Iaddend.
 2. A derailleur for a bicycle according toclaim 1, wherein said linkage members at said linkage mechanism areconnected to said fixing member and movable member through connectingpins, said connecting pins bveing slanted with resepct to a planeperpendicular to the axis of said multistage sprocket assembly so thatsaid forcibly moving mechanism is formed which, when said linkagemechanism is transformed, moves said chain guide axially and radially ofsaid sprocket assembly.
 3. A derailleur for a bicycle according to claim1, wherein said forcibly moving mechanism comprises a first controlmember having a plurality of first engaging portions corresponding tothe number of speed change stages and a second control member having asecond engaging portion engageable selectively with one of said firstengaging portions, one of said first and second control members beingmounted to said fixing member and the other being mounted to saidlinkage mechanism, said guide pulley being adapted to move axially andradially of said multistage sprocket assembly by changing the engagingposition of said second engaging portion with one of said first engagingportions.
 4. A derailleur for a bicycle according to claim 3, whereinsaid first control member is pivoted swingably to said fixing member,said second control member is mounted to said linkage mechanism, saidsecond spring is interposed between said first control member and saidfixing member, and wherein an operating means for transforming saidlinkage mechanism is provided between said first control member and saidlinkage mechanism.
 5. A derailleur for a bicycle according to claim 1,wherein said chain guide is supported swingably to said movable memberthrough said second horizontal shaft at a position shifted from the axisof rotation of said guide pulley.
 6. A derailleur for a bicycleaccording to claim 1, wherein said guide pulley is supported rotatablyto and coaxially with said second horizontal shaft for supporting saidchain guide to said movable member.
 7. A derailleur for a bicycleaccording to claim 1, wherein when said forcibly moving mechanism movessaid guide pulley between a smaller diameter sprocket and a largerdiameter sprocket at said multistage sprocket assembly, said forciblymoving mechanism is adapted to make larger an interval between saidlarger diameter sprocket and said guide pulley than that between saidsmaller diameter sprocket and said guide pulley, whereby resilience ofsaid second spring, when said guide pulley corresponds to said largerdiameter sprocket, is made stronger than that when said guide pulleycorresponds to said smaller diameter sprocket. .Iadd.
 8. A derailleurfor a bicycle according to claim 1, wherein said first spring provides asmaller spring force than said second spring. .Iaddend.